Demolition machine



July 29, 1969 L. A. GRANT 3,458,396 y DEMOLITION MACHINE INVENTOR Louis A. Grunt July 29, 1969 l.. A. GRANT 3,458,396

DEMOLITION MACHINE Filed Sept. 22, 1966 5 Sheets-Sheet 2 iNvENToR Louis A.Gran

July 29, 1969 L. A. GRANT- 3,458,396

DEMOLITION MACHINE Filed Sept. 22, 1966 5 Sheets-Sheet 3 Louis A. Grczim` July 29, 1969 L. A. GRANT 3,458,396

DEMOLITION MACHINE July 29, 1969 l.. A. GRANT 3,458,393

DEMOLITION MACHINE Filed Sept. 22, 1966 5 Sheets-Sheet 5 l Fig |3. 244/ Z24e 32') z 2`. 2481 '[240 +Mw J2; 23s :mi j 3o.`

Louis A. Grunt United States Patent O 3,458,396 DEMOLITION MACHINE Louis A. Grant, Allegheny County, Pa., assignor to Louis A. Grant Inc., Pittsburgh, Pa., a corporation of Penn- Sylvania Filed Sept. 22, 1966, Ser. No. 581,273 Int. Cl. E21c 11/00, 9/00 U.S. Cl. 173-35 14 Claims ABSTRACT F THE DISCLOSURE I disclose, in a demolition machine, the combination comprising a supporting framework, a pair of Outrigger assemblies, means for extendibly mounting said Outrigger assemblies on opposite sides respectively of said supporting framework, a clamping mechanism mounted on each of said outrigger structures, and means for movably mounting a tool supporting member on said framework.

My present invention relates to a demolition machine for a pneumatic or other demolition tool such as a drill, chisel, hammer, or the like, and more particularly to a demolition machine which is capable of both rough and ne adjustment of the demolition tool over a wide work area without resetting the machine therefor and which can =be readily adjusted and/ or anchored as required by specific job size and location.

The invention is particularly adapted for removing the extremely hard debris which accumulates on the bottoms of the soaking furnaces widely used in connection with the steel making process. Such soaking pits are usually arranged in aligned rows thereof and vary between l2 and 20 feet in depth. The soaking pit is usually constructed with a very heavy steel bottom and steel sidewalls, and pig iron or steel ingots are placed in the pits where they are bathed with gas ames or the like to maintain them at elevated temperatures until they can be received at the next station in the steel manufacturing or fabricating process, as the case may be.

Maintaining the ingots at elevated temperatures not only conserves heat Apreviously imparted thereto but in addition prevents cracking or spalling or other malformation resulting from overrapid cooling. During the soaking process and during handling of the ingots as when inserting and removing them from the pit, slag and other surface contamination and foreign matter are removed which collect on the bottom of the pit where, due to the elevated temperatures, these materials are sintered to an extremely hard mass.

Heretofore, a particularly diflicult task has been encountered in the removal of such debris from the bottoms of the soaking pits. To avoid production delays, when such pits need cleaning, this must =be done while the walls and floors of the pits are still at rather high temperatures.

Previously, it has been the practice in most cases to send operating personnel into the pits to manipulate manually within the pits the heavy pneumatic drills, chisels, hammers or the like required to break up the very hard debris covering the floors of the pits.` The use of such tools is rendered quite hazardous because of the high temperature environment, and the time which a single operator could remain in the -pits -without impairment of health and efiiciency was severely limited.

More recently, a crawler-mounted carrier and manipulator structure or chipper carrying one of the aforementioned tools has been proposed for breaking up the hardened material. Such structures had to be rested on the walls dividing the pits and required considerable and expensive wall reinforcement to support the added weight of the crawlers. Moreover, these crawler-mounted structures were cumbersome to move, and diflcult to position for accurate control of the tool carried thereon. This equipment, moreover, could not reach all points of the pit floors eectively and is cumbersome and slow in moving from one pit to the next. Moreover, additional separation between adjoining rows of pits was necessary in some cases to accommodate the crawler. As a result, the widened areas between the -pits required additional structural reinforcement to accommodate the weight of the wider crawlers. Finally, the weight of the cantilevered portions of the crawler-mounted equipment rendered it difficult to make ne adjustments in the placement and in the inclination of the tool to a given location in the oor of the pit.

Still more recently, soaking pit chippers of specialized construction including one or more depending,` extensible booms lwith demolition tools thereon have 'been developed. These demolition machines are intended to cooperate with rails placed along opposite sides of the soaking pit. In one arrangement, the machine is mounted on wheel-supported trucks for engaging the rails and moving the machine along the pits. In another, newer development, the machine is provided with Spanner beams and clamps for engagement with the rails. The last-mentioned machine is moved along the pit and from pit to pit by the overhead crane usually provided for soaking pit operations.

Such demolition machines are described and claimed in a copending application of myself and William H. Bickerstatf, filed lan. 3, 1966, Ser. No. 518,215, entitled Soaking Pit Chipper, on which my present invention constitutes an improvement.

Although the demolition machines described in the aforesaid application have proven to be very successful in practice, in comparison with the prior art, they are relatively cumbersome and expensive to construct and maintain because of the relatively complicated supporting structures involving the aforementioned trucks on the one hand, and on the other a large number of clamping devices and spanner beams. Moreover, the spanner beams must be cut to individual job specifications, depending upon pit dimensions. The square or rectangular conguration of the pits requires a relatively large number of moves or placements of the demolition machine of the aforesaid application in order to reach all areas of a given pit. Finally the particular arrangement of the extensible booms of the earlier machines utilized relatively complex extending means and associated components, all of which are 'bulky and expensive in construction. Moreover for the most arduous pit chipping tasks, the boom arrangement lacks suicient structural rigidity particularly when extended. This applies also to the knuckle joint whereat the demolition tool is pivotally supported.

I have solved the aforementioned difficulties by the provision of a novel arrangement of demolition machine wherein a turntable or similar support is rotatably or otherwise movably mounted on the machine supporting structure, and the structure is provided with an extendable Outrigger assembly at opposite sides thereof. The Outrigger assesmblies enable the machine to be readily used for cleaning soaking pits of differing widths. A clamp mechanism is installed on each of the Outrigger assemblies and can be quickly and efficiently operated for securing and releasing the machine from the coping rails or other supporting means which are normally provided along opposite sides of the soaking pit furnace. With this arrangement, when the machine is used for cleaning the soaking pits, the machine can be quickly and easily moved to all parts of the soaking pit to cover the door area thereof within a shorter time. Likewise the demolition machine can be utilized in pits of differing sizes without the necessity of cutting individual lengths of spanner beams. In either case the extendable outriggers and clamps permit the machine to be quickly adjusted to the width of the soaking pit without the necessity of loosening and tightening a relatively large number of clamping devices. Moreover, it is contemplated that the Outrigger clamp can be manipulated remotely, if desired, so that novel pit chipper can be moved along a given pit or from pit to pit without exposing workmen to the heat thereof.

A novel extensible boom assembly is mounted in depending relationship on the aforementioned turntable and is provided on its extensible end with a suitable tool for breaking up the soaking pit debris and other demolition operations. In one arrangement thereof the boom assembly is extendable by means of a novel telescoping arrangement, in other arrangements by means of a unique knuckle joint assembly and in still other arrangements by a combination of these. In addition, means are disclosed for pivotally securing the demolition tool to the extendable end of the boom assembly to provide a more rigidized and structurally stable support therefor. The turntable is rotated, the boom assembly is assembled to the underside thereof, and the demolition tool otherwise is mounted on the boom assembly in much the same manner as disclosed in the aforementioned copending application.

In still other arrangements of my novel pit chipper structure, elongated track means are provided which extend generally between the extendable outriggers, and the turntable rotating and supporting mechanism is mounted for movement along the track means so that the turntable and related components including the boom assembly can traverse a major proportion of the demolition machine to aid in the placement of the demolition tool carrier and boom assembly.

During the foregoing discussion various objects, features and advantages of the invention have been alluded to. These and other objects, features and advantages of the invention together with constructural details thereof will be elaborated upon during the forthcoming description of presently preferred embodiments of the invention and presently preferred methods of practicing the same.

In the accompanying drawings I have shown certain presently preferred embodiments of the invention and have illustrated certain presently preferred methods of practicing the same, wherein:

FIGURE 1 is a top plan view of one form of demolition machine constructed in accordance with my invention and arranged particularly for soaking pit cleaning but suitable for other demolition operations;

FIGURE 2 is a side elevational view of the demolition machine shown in FIGURE 1;

FIGURE 3 is a right end elevational view of the machine as shown in FIGURE 2;

FIGURE 4 is a top plan view of the boom assembly as shown in FIGURE 2 and taken generally along reference line IV--IV thereof;

FIGURE 5 is a side elevational view of the boom assembly as shown in FIGURE 4;

FIGURE 6 is a cross-sectional view of the -boom assembly as shown in FIGURE 5 and taken along reference line VI--VI thereof;

FIGURE 7 is a partial longitudinal sectioned view of the boom assembly as shown in FIGURE 4 and taken generally along reference line VII-VII thereof;

FIGURE 8 is a schematic diagram of one arrangement of fluid circuit for operating and remotely controlling a demolition machine in accordance with my invention;

FIGURE 9 is a similar view of still another form of novel boom assembly;

FIGURE 10 is a similar view of still another arrangement of my novel boom assembly;

FIGURE 11 is a top plan view illustrating another form of my novel demolition machine wherein the turn` table and boom assembly are arranged for traversing the supporting structure of the machine;

FIGURE 12 is a cross sectional view of the demolition machine of FIGURE 11 and taken along reference line XII-XII thereof;

FIGURE 13 is a top plan view of still another form of my novel demolition machine; and

FIGURE 14 is a front elevational view of the machine as shown in FIGURE 13.

Referring now more particularly to FIGURES 1-3 of the drawings, the exemplary arrangement of my novel demolition machine shown therein comprises an elongated supporting framework 10 on which is mounted a platform 12 and extendible Outrigger supports 14 and 16 mounted adjacent the ends respectively of the framework 10. As better shown in FIGURES 2 and 3 a plate member of turntable 18 is rotatably or otherwise movably depended from the platform 12 which includes in this example an upper supporting plate 20, a lower supporting plate 22 and a supporting cylinder 24 which extends through suitable apertures in the upper and lower plates 20, 22 and is rigidly secured thereto, as by welding.

In the present arrangement of my invention the framework 10 further includes a pair of beam members 26 and 28, together with the upper and lower plates 20 and 22. Desirably the beams 26, 28 are provided in the form of rectangular or square tubing and are joined respectively to the upper and lower end portions, as viewed in FIG- URE 1, of the platform plates 20, 22 to complete the framework 10.

Each Outrigger assembly 14 and 16, in this example, includes an end brace extending transversely of the platform 10, to which end brace a pair of complementarily smaller beam members 32 and 34 are joined respectively at the ends of the end brace 30. Desirably the beams 32 and 34 are likewise of square or rectangular configuration and are aligned with the adjacent open ends of the beams 26, 28. When thus arranged the Outrigger beams 32, 34 can be extensibily or telescopingly inserted into the associated ends of the platform beams 26 or 28. With this arrangement the outrigger means 32, 34 are slidably mounted within the end portions of the platform beams 26, 28. Of course the platform beams can similarly be inserted or telescoped into the Outrigger beams, if the latter can be complementarily larger.

If desired, a pair of operating cylinders 36 can be coupled to each of the platform beams 26, 28 and to the associated supporting beams 32 or 34 of the Outrigger assemblies 14, 16 to extend and retract automatically and remotely the outriggers 14, 16 relative to the platform 12. To conserve space, the cylinder 36, if used can be located within the hollow beams 26, 28 and 32, 34.

In accordance with another feature of the invention means are mounted on each Outrigger assembly 14 or 16 for quickly and releasibly clamping the platform 10 to coping rails 37 and 38 or other supporting means usually mounted along the top surfaces of wall structures separating the soaking pits so as to be disposed on opposite sides of a given soaking pit.

As better shown in FIGURE 3 one form of such clamping means includes an actuating cylinder 40 pivotally supported adjacent its upper end, as denoted by reference character 42, to the end brace 30 of each Outrigger assembly. To effect clamping, the distal end of piston rod 44 has rigidly secured thereto a clamp or foot plate 46, which when the cylinder 40 is pivoted inwardly to a generally vertical position as better shown in FIGURE 2, becomes engaged under the bottom flange of the associated coping rail 37 or 38. The cylinder 40 is constructed in a conventional manner in order to mechanically and hydraulically absorb the j rather large upward separatory forces applied to one or both of the Outrigger assemblies Because the aforementioned separatory forces, which tend to lift the framework including the outrigger assemblies 14, 16 from the coping rails 37, 38 may be rather severe, the end braces 42 desirably are provided with an arched configuration as better shown in FIGURE 3 to provide the necessary strength. In this example the end braces are fabricated from a pair of spaced, generally arch-shaped plates 52 having the configuration shown in FIGURE 3 and secured in spaced relationship by spacer plates 54. The clamping cylinder is secured to a spacer bracket 56 secured between the uppermost or keystone areas of the arch plates 52. At their ends the plates 52 are joined to the ends of the Outrigger beams 32, 34 respectively by means of pairs of bracket plates 58, 60 and Istructural tubular sections 62 and 64. In this example bars 66 can be provided in the outer end portions of the Outrigger beams 32, 34 to facilitate grasping the outriggers 30 by hand or with a crane hook or other tool for extending or retracting the outriggers 30, as ybetter shown in FIGURES l and 3. A

Also mounted on the upper side of the platform 10 are a hydraulic storage tank 68 for the hydraulic circuit described below in connection with FIGURE 8 and an associated accumulator tank 70 and motor pump 72 for the hydraulic circuit. The motor pump 72 is mounted upon the lower supporting plate 22, and the storage tank 68 is `supported by an auxiliary supporting plate 74 while the accumulator 70 is secured to the outer side of one of the platform beams, for example the beam 26.

To the undersurface of turntable 18 are secured a pair of depending supporting brackets 76 with bushings 78, which engage trunnion pin 80 inserted through boom assembly bracket 82. The boom assembly 48 is thus pivotally joined to the turntable 18 and is pivoted by cylinder 84 and extended by cylinder 86 in much the same manner as set forth .in the aforementioned copending application. Similarly, tool cradle 88 is pivotally joined at knuckle joint 90 to the outer end of the inner boom section 92 and pivoted by cylinder 94 as described in the aforesaid Grant et al. application.

The turntable 18 is secured to an inner supporting cylinder 96 for rotation therewith by a transmission denoted generally by reference character 98. The inner supporting cylinder 96 is rotatably supported and stabilized within the outer Isupporting cylinder 24 by means of sleeve and X-bearing (not shown) for rotation by the transmission 98 substantially as set forth in the aforementioned copending application. The necessary hydraulic connections to the boom assembly 48 and related components are provided through a conventional hydraulic swivel coupling 100 mounted in this example on the upper end of the stationary stabilizing bearing sleeve 102.

Referring now to FIGURES 4-7 of the drawings one exemplary arrangement of my novel extensible boom assembly is illustrated therein. The boom assembly 48 thus comprises an outer, pivoted boom section 104 having the aforementioned supporting and pivot bracket 82 mounted thereon, and an inner extensible or telescoping boom section 106. The inner boom section in this example is slidably mounted within the outer boom section 104 by means of a unique arrangement of bearing members which permit extension and retraction of the telescoping inner boom section 106 under extremely heavy loads frequently encountered in soaking pit chipping or other demolition operations. In this example a iirst wearing strip arrangement is provided for absorbing the relatively greater forces exerted upon the demolition tool in this example in the vertical direction, while a second wearing 'strip arrangement is utilized for the relatively lighter forces exerted laterally upon the tool. It Will be understood of course as this description proceeds that the aforementioned first and second wear-ing strip arrangements can be interchanged depending upon the application of the invention and the direction in which maximum forces are exerted, or alternatively either of the rst or the second wearing CII strip arrangements can be duplicated where force-s in the vertical and lateral directions are approximately equal.

One example of rst wearing strip arrangements includes a first group of relatively short elongated strips 108 mounted on the upper and lower inner surfaces of the outer boom section 104 adjacent the front or tool end thereof. A second group of wearing strips 110 are mounted on the upper and lower outer surfaces of the inner boom section 106 adjacent the rearward end thereof. Desirably the wearing strips 108, 110, to which the greater forces are applied, are fabricated from brass or other suitable bearing material. In this arrangement the strips 108 and 110 need not extend the full length of either of the boom sections 104, 106 owing to the displacement of the load bearing portion of the inner -boom section relative to the outer boom section as the former is extended and retracted.

On the other hand the relatively lighter lateral boom forces are absorbed by the aforementioned second wearing arrangement with a pair of such strips 112 being secured to each of the outer lateral surfaces of the inner boom section 106, as better shown in FIGURES 5 and 6 of the drawings. In one example of the second or lateral wearing strips, the strips 112 as better shown in FIGURE 6 are of angle iron construction and extend substantially along the entire length of the inner boom section 106 in a spaced generally parallel array. In this example, the strips 112 can be fabricated from carbon steel owing to their greater length and the aforementioned relatively lighter lateral forces encountered in this application of the invention.

The wearing strips 108, 110 for vertical loads are secured as aforementioned to the respective boom sections, as by mounting bolts respectively, while the lateral strips 112 are secured by welding. The use of the angle iron construction of the lateral strips 112 affords the necessary resiliency to prevent binding or spalling of similar structural materials, i.e., carbon steel, of the outer boom section and the strip-s 112. Thus, it is not necessary to employ one of the more expensive bearing metals in the fabrication of the lateral strips 112. Obviously of course the strips 112 can be secured to the outer boom section 104 for engagement with the inner section.

As also shown in FIGURES 4, 5 and 7 of the drawings my novel boom assembly further includes a unique arrangement which trunnion pin 118 (FIGURE 2) of the tool cradle 88 is secured. In furtherance of this purpose a pair of similarly shaped gusset plates 120 (FIGURE 4) having bushing supporting extensions 122 and bushings 124 thereon are secured to the lateral end portions of the inner boom section 106. The gussets 120 are reinforced by a supporting housing the ends of which are closed by the gusset plates 120, with the top, bottom and side `Walls thereof being formed by plates 126, 128, and 132 respectively, as better shown in FIGURE 7. The top wall of the housing is completed by the adjacent undersurface 134 of the inner boom section 106. To the side wall 130 are secured a pair of bushing supports 136, which are extended in general alignment with their ends joined to a single bushing 138, although a pair of bushings (not shown) can be substituted. The bushings 124, 138 together with their associated components, thus present a multiple point support for the trunnion pin 118 which is inserted through the aforesaid bushings and through suitable apertures of the tool cradle 88 when aligned therewith. The tool cradle support thus secured to the outer end of the inner boom section 106 is thereby rendered capable of absorbing extremely large reactive forces imparted thereto by the demolition tool and by manipulation of the boom assembly.

Depending upon the specific application of the invention and the particular boom structure utilized one of those tool cradles can be employed, which are described and claimed in my copending application entitled Demolition Tool Cradle tiled Ian. 7, 1966, Ser. No. 519,211 and now Patent No. 3,389,755 or in my copending appli- 7 cation entitled Blast Furnace Lining 'Removing Machine, led Aug. 8, 1966, Ser. No. 573,758 and noW Patent No. 3,346,300.

Referring now to FIGURE 8 of the drawings, an exemplary form of hydraulic circuit is illustrated therein for actuating the demolition machine described above in connection with FIGURES 1-3 or -below with reference to FIGURES 12 and 13. In this arrangement, the boomY hoist cylinder 84, the telescoping cylinder 86 and the tool cradle cylinder 94 are coupled to the aforementioned hydraulic swivel 100 at the movable ports 140 thereof. Stationary swivel ports 142 are coupled to holding valves 144, 146 and 148 which thus maintain the positions imparted to the cylinders 84, 86 and 94 respectively. Valves 144-148 along with turntable holding valve 150 can be stationarily mounted on the machine platform as better shown in FIGURE l, or alternatively the holding valves 144-150 can be combined (not shown) with mobile valve stack 152, containing solenoid valves 154, 156, 158, 160 coupled respectively to the holding valves 144- 150. Each of the solenoid valves included a pair of conventional actuators (not shown) for operating the cylinders 84, 86 and 94 and the drive motor 164 forming part of the transmission 98 l(FIGURE 1), in either direction of travel thereof. Accordingly valves 154-160 respectively control raising and lowering of the boom assembly 48 by means of cylinder 84, extension and retraction of the inner boom 106 (FIGURE 6) by means of cylinder 86, pivoting of the tool cradle 88 by means of cylinder 94 and rotation or swing of the boom assembly and supporting turntable 18 by means of hydraulic motor 164 and transmission 98.

The valve stack 152 preferably is coupled to the holding valves 144-150 by elongated flexible conduits so that the demolition machine can be operated from a remote location as desired. The valve stack 152 desirably includes additional valves 166 and 168 for operating the clamping cylinders 40 of Outrigger 30 and for actuating the air hammer 50 or the like mounted on the tool cradle 88. Valve 166 is a conventional lever-operated hydraulic detent valve connected directly to the cylinders 40 in parallel, as shown. On the other hand, conventional air valve 168 is coupled to an external source 169 of compressed air and to the swivel 100 and thence to air hammer cylinder 171.

The necessary hydraulic fluid for the aforementioned operation is supplied to the valve stack 152 (excepting air valve 168) through conduit 170 (to which is connected the accumulator tank 70) by motor-pump 72 extracting hydraulic fluid from reservoir 68 through conduit 172. The hydraulic pressure in conduit 170 is maintained substantially constant by regulator 173. The pump output is by-passed back to the reservoir tank 68 through conduit 74 and presettable pressure relief valve 176 for adjusting the operating pressure in the system. The relief valve 176 can be operated through conduit 178 coupled downstream of check valve 180. The hydraulic fluid supplied to the valve stack 152 is continually returned to the reservoir 68 through conduit 181. An additional, by-pass return conduit 183 is provided between the valve stack 152 and the storage tank 68 for relieving overpressures developed in one or more of the valves of the valve stack during use of the demolition machine, for example by prying operations with the tool 50.

Referring now to FIGURES 9 and l0 of the drawings alternative forms 182 and 184 respectively of the boom assembly are shown therein. Each of the boom assemblies 182 and 184 are joined to the undersurface of turntable 18' or 18 as that described in connection with FIGURE 1 to 3 of the drawings. In order to afford differing ranges of operation to the boom assemblies 182 and 184 respectively the asembly 184 is pivotally mounted on a generaly vertical bracket structure 76' similar to that described in connection with FIGURES 2 and 3 of the drawings. On the other hand, boom assembly 182 is pivotally mounted at 186 on an angularly disposed bracket aS- sembly 188, which is otherwise similarly secured to the underside of the turntable 18'.

The boom assemblies 182 and 184, as shown in FIG- URES 9 and 10 respectively of the drawings, are provided with an additional knuckle joint 190 or 192 respectively whereby the tool cradle 88 secured to the boom assembly 182 or 184 can be extended within the limits of the assembly without the necessity of providing telescoping boom sections. Retraction of the tool 50' is performed by bending the knuckle joint 190 or 192 in one direction while pivoting the cradle joint 118' in the opposite direction. Extension of the tool 50' is subsequently accomplished by straightening out the aforementioned joints. The dilfering configurations of brackets 194 and 196 of boom sections 198 and 200 respectively, together with the differing conligurations of the supporting brackets 188 and 76 respectively impart differing ranges of operation to the respective boom assemblies 182, 184 as denoted by arcs 202 associated with boom assembly 182 and arcs 204 with boom assembly 184.

It will be understood of course that any one of the boom assemblies illustrated in FIGURES 4 to 7, 9 and 10 can be utilized -with any one of the forms Of my demolition machine as shown in FIGURES 1-3, 11-12, and 13-14 respectively. It will be also understood that the hydraulic control circiut of FIGURE 8 can be utilized any of the aforementioned forms of my machine.

Although my demolition machine has been described primarily in connection with cleaning soaking p'it furnaces, obviously there are many other applications, such as delining blast furnaces, ladles and the like. Further, I contemplate substituting a scoop, backhoe, bucket, or other excavating tool or implement for the demolition tool 50 for excavating operations, such as digging foundation holes and the like. In the latter connection each of the outriggers 14, 16 can be mounted on a wheelor crawlersupported truck or the like to add mobility to the demolition machine in applications where a suitable crane or hoist is not available. Therefore the terms demolition tool as used herein is intended to be inclusive of various excavating implements.

It is also contemplated, in those applications wherein the Outrigger assemblies 14 and 16 are not fully extended when the demolition machine is properly positioned over a soaking pit or other work area, that the Outrigger cylinders can be actuated, after the clamping mechanisms 40-46 thereof have been securely placed, to cause the platform 12 to traverse portions of the Outrigger beams 32, 34. For example the cylinders 36a can be extended and the cylinders 36h retracted to slide the platform beams 26, 28 to the right over the Outrigger meams 32, 34. Opposite actuating of the cylinders 36a, 36b causes the platform 12 to move to the left, as viewed in FIGURES 1 and 2. These platform movements also move the platform 18, boom assembly 48, and tool 50 suspended from the platform 12 to provide a correspondingly greater range of coverage by the tool 50 and the extensible boom 48. As a result, the number of placements of the demolition machine for a given work area are further reduced.

Referring now to FIGURES 11 and 12 of the drawings wherein similar reference characters with primed accents refer to similar components of FIGURES l to 3, another arrangement of my demolition machine 10 includes means incorporated therein for causing the turntable 18' and associated supporting structure therefore to traverse the length of the platform beams 26', 28. One arrangement of such means includes a track plate 210 secured in this example to the inwardly facing wall of each of the platform beams 26', 28. The track plates 210 desirably are reinforced at intervals along their lengths by a plurality of gussets 212. To prevent the beams 26. 28' from canting under the weights born by the track plates 210, a pair of I-beams 214 or the like are secured transversely of the beams 26', 28 adjacent the respective ends thereof. Turntable supporting cylinder 24 is similarly supported from upper and lower platform plates 20', 22. The lower plate 22 in this arrangement terminates short of the platform beams 26', 28', while the upper plate spacedly overlies the beam 26', 28' to prevent dirt and debris from collecting on the track plates. Thus, the upper and lower plates 20', 22' are joined to a movably mounted framework 12' fabricated in this example from pairs of lateral and transverse channel rbe'ams 216, 218, respectively. If desired captaive rails (not shown) can be spacedly mounted over the rollers 220 to prevent substantially upward displacement ofthe framework 12'.

The movable platform 12' is supported at each lateral side thereof by a number of rollers 220 and shafts 222 affixed to the rolers 220 for rotation therewith. The shafts 222 are rotatably mounted on the respectively associated channel beams 216 and are driven in this example by air motors 224. With this arrangement the movable platform 12' can be propelled in either direction along the track plates 210, i.e. toward one 'of the other of outriggers 30', within the limits established by the I-beams 214. This arrangement permits the tumtable 18 and the boom and demolition tool assembly secured thereto to be moved toward either lateral wall of even the wider soaking pits, where the outriggers 30 may be substantially fully extended. If desired, Outrigger operating cylinders 36 (not shown in FIGURE 11) can be provided as described in FIGURE 3 of the drawings.

Referring now to FIGURES 13 and 14 of the drawings another exemplary arrangement of my demolition machine is shown therein and is generally similar to the organization of my machine as depicted in FIGURE l of the drawings. The turntable supporting platform 12' 'thus includes upper and lower supporting plates 20', 22', with the upper plate being provided with four apertured lifting lugs 230 for engagement by the aforementioned crane or the like in placing the machine 10'. Similar lifting lugs are shown in FIGURES 1-3 of the drawings. Outrigger beams 32', 34' are each provided with an array of apertures 232 as better shown in FIGURE 13 which are successively alignable with an aperture 234 in the associated end of one of the platform `beams 26', 28'. When each Outrigger 30' has been extended to the desired distance one of the apertures 232 in each of its associated beams 32 and 34 are alignable with the respectively associated apertures 234, and suitable pins (not shown) are inserted therethrough to secure the outriggers 30' against further, inadvertent movement. At such positions of the outriggers 30 their clamping means 40 are actuated to secure the outriggers 30 to the coping rails 37', 38 or the like,

It will be understood of course that the demolition machine 10" of FIGURES 13 and 14 can be provided with outrigger cylinders 36 (FIGURES 1-3) or with the movable platform assembly 12' of FIGURE 11, or both.

Mounted on the upper surface of the upper platform' plate 20' are a pair Of motor driven winches 236 and 238. Each of the Winches includes a cable drum 240 on which is wound cable 242 of sufficient length to permit securance thereof to a lug or hook 244 permanently mounted in this example at each end wall 246 of the soaking pit furnace or the like. By operation of one or other of the winch motors 248 the associated cable can be wound upon its drum 240 to draw the demolition machine 10', after loosening its clamp means 40', along the coping rails 37', 38' toward one or other of the pit end walls 246. In the case of soaking pit cleaning operations this arrangement eliminates further useage of the aforementioned crane, after the initial placement thereby of the machine 10' on the soaking pit coping rails. For subsequent placements or movements of the demolition machine 10', the latter can be drawn along the length of the soaking pit by use of one or both of the Winches 236, 238.

As better shown in FIGURE 14 of the drawings the last-described arrangement of my demolition machine 10 can be provided with a knuckle-jointed type of extendible boom assembly 182', similar to the assembly 182 of FIG- URE 9. It is understood, of course, that an extendible boom assembly of the telescopng type such as the assembly 48 of FIGURES 1-7 can be substituted, or that the boom assembly 182 can be further provided with a telescoping section (not shown) in addition to its knucklejointed sections.

FIGURE 14 further illustrates the manipulative steps imparted to the boom assembly 182' in performing soaking pit cleaning operations. The coverage of work area of the demolition machine is considerably extended by rotation of the turntable 18', irrespective of whether the boom assembly 182' or 48 or equivalent is utilized.

From the foregoing it will be apparent that novel and eflicient demolition machines have been described herein together with novel and eilicient forms of boom assemblies and control circuits for use therein. While I have shown certain presently preferred embodiments of the invention and have illustrated certain presently preferred methods of practicing the same, it is to be distinctly understood that the invention may be variously embodied and practiced without departing from the spirit and scope of the impended claims.

I claim:

1. In a demolition machine the combination comprising a supporting framework, a pair of Outrigger assemblies, means extendibly mounting said Outrigger assemblies on opposite sides respectively of said supporting framework for longitudinally outward extension of said assemblies beyond said sides respectively, a clamping mechanism mounted on each of said Outrigger structures for movement therewith for clamping an external support for said framework between said mechanism and the associated one of said assemblies, and means for movably mounting a tool supporting member on said framework.

2. The combination according to claim 1 wherein said clamping mechanism each include a piston and cylinder arrangement having a clamping member on the distal end of a piston rod forming part of said arrangement.

3. A combination according to claim 1 wherein said framework includes a pair of spaced generally parallel beams, and each of said Outrigger assemblies including a pair of similarly spaced complementarily shaped beams slid-ably mounted on the adjacent end portions of said framework.

4. The combination according to claim 1 wherein each of said Outrigger assemblies includes arched plate means extending generally parallel to the adjacent side of said framework structure and movable with the associated assembly, and said clamping mechanisms are pivotally joined respectively to said arched plate means at the keystone areas thereof.

5. The combination according to claim 3 wherein said framework beams are of tubular configuration and said Outrigger beams are telescopically inserted into the associated ends respectively of said framework beams.

6. The combination according to claim 5 wherein motive means are operatively coupled to said Outrigger beams and to said framework beams for extending and retracting said Outrigger assemblies relative to said framework.

7. The combination according to claim 1 wherein said tool supporting member is a turntable rotatably mounted in depending relationship to said framework.

8. The combination according to claim 7 wherein an extendible boom assembly is pivotally mounted on the undersurface of said turntable, and a tool supporting cradle is pivotally mounted on the extendible end of said boom assembly.

9. The combination according to claim 8 wherein said extendible boom assembly includes telescopng inner and outer boom sections, said inner boom section being slidably mounted within said outer boom section by a plurality of wearing strips secured to at least one of said boom sections.

10. The combination according to claim 8 wherein the pivot mounting of said tool cradle is reniforced by a pair of gusset plates spacedly secured to the extendible end of said boom assembly, each of Said gusset plates terminating in an extension with a bushing thereon, transversely extending reinforcing plates secured at their opposite ends to said gusset plates, additional extensions secured to at least one of said transverse plates and extending Vgenerally in parallel alignment with said gusset plate extensions, additional bushing means mounted on said additional extensions in spaced alignment with said bushings, said tool cradle having pivot connections inserted respectively between said bushings and said bushing means, and a trunnion pin inserted therethrough for pivotally joining said cradle to said bushings and bushing means.

11. The combination according to claim 8 wherein said boom assembly includes a plurality of interconnected pivoted sections, a demolition tool cradle is pivotally connected to the outer end of the outermost one of said pivoted sections, and means are provided for pivoting each of said boom sections and said tool cradle.

12, The combination according to claim 8 wherein fluid actuated cylinders are provided for pivoting and extending said boom assembly and for pivoting said tool cradle, conduit connections therefor coupled to a uid swivel coupling mounted adjacent said turntable, an actuating uid reservoir and motor pump unit therefor are mounted on said framework, fluid actuated drive means are provided for said turntable on said platform, a remotely operable valve stack is provided having flexible conduit connections therefrom to said swivel coupling and to said drive means and said cylinders for remotely actuating said drive means and said fluid actuated cylinders, a flexible supply conduit conection is provided between said reservoir and said valve stack for supplying actuating uid thereto, said clamping mechanisms including a uid actuated cylinder, a fluid actuated demolition tool mounted on said tool cradle and said valve stack including additional valves and flexible conduits for actuating said demolition tool and said clamping mechanisms remotely, and respectively.

13. In a demolition machine the combination comprising an elongated supporting framework, a pair of Outrigger assemblies, means for extendably mounting said Outrigger assemblies on the ends respectively of said framework, means for movably mounting a tool supporting member on said framework, for longitudinal displacement therealong, and clamping means movable with each of said outrigger assemblies for clamping an external support for said framework between said clamping means and the associated one of said assemblies.

14. In a demolition machine the combination comprising an elongated supporting framework, a supporting plat form rotatably mounted on the undersurface of said platform, a demolition tool assembly pivotally mounted on said platform, a pair of oppositely driven Winches and cable drums mounted on said framework, cables wound upon said drums respectively and attachable to external anchor members remotely placed on opposite sides respectively of said machine for drawing said framework back and forth between said anchor means and along external support means by operation of said Winches, and clamping means secured to said framework for clamping said framework to said support means at a selected position therealong.

References Cited UNITED STATES PATENTS 350,090 9/1886 White 188-43 1,767,795 6/1930 Huff. 2,623,739 12/1952 Thomas et al 173-35 X 3,247,979 4/ 1966 Melton et al. 3,346,300 10/ 1967 Grant 299-70 3,354,967 11/1967 Skendrovic 173-43 602,125 4/1898 Burrows 182-128 X 3,370,654 2/ 1968 Skendrovic 299-70 X FOREIGN PATENTS 1,180,090 3/1960 France.

134,704 1961 U.S.S.R.

ERNEST R. PURSER, Primary Examiner U.S. Cl. X.R. 

